EP0531088B1 - Dispositif de transmission de puissance pour entraînement à quatre roues motrices - Google Patents

Dispositif de transmission de puissance pour entraînement à quatre roues motrices Download PDF

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Publication number
EP0531088B1
EP0531088B1 EP92307919A EP92307919A EP0531088B1 EP 0531088 B1 EP0531088 B1 EP 0531088B1 EP 92307919 A EP92307919 A EP 92307919A EP 92307919 A EP92307919 A EP 92307919A EP 0531088 B1 EP0531088 B1 EP 0531088B1
Authority
EP
European Patent Office
Prior art keywords
output shaft
planetary gear
gear unit
carrier
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92307919A
Other languages
German (de)
English (en)
Other versions
EP0531088A1 (fr
Inventor
Kenji Shimizu
Kazuhito Ikemoto
Masahiro Moritani
Yasuyuki Iida
Tomoyuki Kanou
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP22156791A external-priority patent/JP2979762B2/ja
Priority claimed from JP3267222A external-priority patent/JP3003330B2/ja
Application filed by Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP0531088A1 publication Critical patent/EP0531088A1/fr
Application granted granted Critical
Publication of EP0531088B1 publication Critical patent/EP0531088B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3462—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear with means for changing distribution of torque between front and rear wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3467—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear

Definitions

  • the present intention relates to a power transfer device adapted for use in-combination with a primary transmission for four-wheel drive vehicles.
  • a power transfer device adapted for use in combination with a power transmission, which comprises a housing adapted to be secured to one end of the power transmission casing, a first output shaft rotatably mounted within the housing for drive connection to a set of rear road wheels, a second output shaft rotatably mounted within the housing in parallel with the first output shaft for drive connection to a set of front road wheels, a center differential in the form of a planetary gear unit mounted on the first output shaft to transfer input drive torque to the first and second output shafts, a drive sprocket rotatably mounted on the first output shaft and drivingly connected to a driven sprocket mounted on the second output shaft, and a changeover mechanism mounted on the first output shaft to selectively transfer the drive torque from an output element of the planetary gear unit to the drive sprocket.
  • the planetary gear unit includes a carrier having a tubular hub portion arranged in surrounding relationship with the first output shaft and associates with the changeover mechanism, and the drive sprocket is arranged between the planetary gear unit and the changeover mechanism and rotatably supported on the tubular hub portion of the carrier.
  • it is required to supply lubricating oil into double spaces among the first output shaft, the tubular hub portion of the carrier and the drive sprocket, and it is also required to assemble a bearing respectively within the double spaces among the first output shaft, the tubular hub portion of the carrier and the drive sprocket. This results in a complicated mounting construction of the drive sprocket.
  • US-A-4,878,399 illustrates a power transfer device in accordance with the preamble of Claim 1 but in which the input torque is always transmitted to two sets of road wheels through a carrier for planet gears.
  • a primary object of the present invention to provide an improved power transfer device wherein the drive sprocket can be mounted on the first output shaft in a simple construction without causing such a problem as described above.
  • a secondary object of the present invention is to provide an improved power transfer device wherein a changeover mechanism for the center differential can be manufactured in a simple construction.
  • the primary object is accomplished by providing a power transfer device in accordance with Claim 1.
  • Fig. 1 illustrates a power transfer device for an automotive vehicle of the part-time four-wheel drive type.
  • the power transfer device has a housing 11 secured to a easing C of a primary power transmission of the vehicle and includes, as main components, an input shaft 12, a first output shaft 13, a second output shaft 14, an ancillary change-speed mechanism 20 in the form of a planetary gear unit, a first changeover mechanism 30 for the planetary gear unit 20, a center differential 40, a second changeover mechanism 50 for the center differential 40, a drive mechanism 60 for the second output shaft 14 and a third changeover mechanism 70 for selectively establishing a two-wheel drive train or a four-wheel drive train.
  • the input shaft 12 is rotatably supported on a left-hand side wall of the housing 11 through a needle bearing, a carrier 22 of the planetary gear unit 20 and a ball bearing.
  • the input shaft 12 has an internally splined portion for connection to an output shaft (not shown) of the primary power transmission and has an externally splined portion 32 for mounting the planetary gear unit 20 thereon.
  • the first output shaft 13 is rotatably supported on a right-hand side-wall of housing 11 through a ball bearing and is arranged coaxially with the input shaft 12 for drive connection to a set of rear wheel drive axles (not shown).
  • the first output shaft 13 has an inner end portion coupled within a hollow inner end portion of input shaft 12 through a needle bearing for relative rotation.
  • the second output shaft 14 is arranged in parallel with the first output shaft 13 and is rotatably mounted within the housing 11 through a pair of axially spaced ball bearings for drive connection to a set of front wheel drive axles (not shown).
  • the planetary gear unit 20 comprises a sun gear 21 mounted in place on the externally splined portion 32 of input shaft 12 for rotation therewith, a stationary ring gear 24 arranged concentrically with the sun gears 21 and secured to an internal cylindrical wall of housing 11, a plurality of planetary gears 23 rotatably supported by the carrier 22 and in mesh with the sun gear 21 and ring gear 24, and an internally splined side member 33 integrally fixed to the right end of carrier 22 for rotation therewith.
  • the first changeover mechanism 30 is arranged adjacent the planetary gear unit 20 to selectively establish high and low speed drive power trains.
  • the first changeover mechanism 30 includes an internally splined clutch sleeve 34 axially slidably mounted on a tubular output member 15 which is rotatably mounted on the first output shaft 13.
  • the clutch sleeve 34 has an internal spline 31 engageable with the externally splined portion 32 of input shaft 12 through a synchronizer assembly and has an external spline engageable with the internal spline of side member 33.
  • the clutch sleeve 34 When retained in a first position as shown by a solid line in Fig.2, the clutch sleeve 34 is disengaged from the internal spline of side member 33 and engaged with the externally splined portion 32 of input shaft 12 at its internal spline 31 to effect direct connection between the input shaft 12 and the tubular output member 15 thereby to transfer drive torque from the input shaft 12 to the output member 15 at the same speed as that of input. shaft 12.
  • the clutch sleeve 34 When shifted to and retained in a second position as shown by an imaginary line in Fig. 2, the clutch sleeve 34 is disengaged from the externally splined portion 32 of input shaft 12 and engaged with the internal spline. of side member 33 at its external spline to drivingly connect the input shaft 12 to the output member 15 through the planetary gear unit 20 thereby to transfer the drive torque from input shaft 12 to the output members 15 at a predetermined reduction speed ratio.
  • the center differential 40 is in the form of a planetary gear unit of the double pinion type which comprises a sun gear 41 integrally formed with the first output shaft 13, a carrier 42 rotatably mounted at its right-hand hub-portion on the first output shaft 13 through a needle bearing for relative rotation, a plurality of internal planetary gears 43a rotatably supported by the carrier 42 and in mesh with the sun gear 41, a plurality of external planetary gears 43b rotatably supported by the carrier 42 and in mesh with the internal planetary gears 43a, and a ring gear 44 concentrically assembled with the carrier 42 and in mesh with the external planetary gears 43b.
  • the second changeover mechanism 50 is arranged between the first changeover mechanism 30 and thee center differential 40 to selectively effect differentiation between the first and second output shafts 13 and 14. As shown in Figs. 3 and 4, the second changeover mechanism 50 includes a clutch sleeve 55 axially slidably mounted on the tubular output member 15.
  • the clutch sleeve 55 has an internal spline 55a in continual engagement with an externally splined portion 51 of tubular output member 15 and engageable with an externally splined portion 56 of first output shaft 13 and has an external spline 55b in continual engagement with an internally splined portion 54 of a slide member 53 of ring gear 44 and engageable with an internal spline 52 formed on the left-hand portion of carrier 42.
  • the internal spline 55a of clutch sleeve 55 is chamfered only at its right end for smooth engagement with the external splined portion 56 of first output shaft 13, while the external spline 55b of clutch sleeve 55 is also chamfered only at its right end for smooth engagement with the internal spline 52 of carrier 42.
  • the clutch sleeve 55 is disengaged from the externally splined portion 56 of first output shaft 13 and the internally splined portion 52 of carrier 42 and maintained in engagement with the internally splined portion 54 of side member 53 to drivingly connect the tubular output member 15 to the carrier 42 and the first output shaft 13 through the center differential 40 thereby to effect, differentiation between the first and second output shafts 13 and 14.
  • the drive mechanism 60 includes a drive sprocket 61 rotatably mounted on the first output shaft 13, a driven sprocket 62 integrally provided on the second output shaft 14 for rotation therewith and a drive chain 63 stretched over the drive and driven sprockets 61 and 62.
  • the third changeover mechanism 70 is arranged between the center differential 40 and the drive sprocket 61 and mounted on the first output shaft 13 to selectively transfer the drive torque from the right-hand hub portion of carrier 42 to the second output shaft 14 through the drive mechanism 60. As shown in Fig.
  • the third change-over mechanism 70 includes an externally splined hub member 71 fixedly assembled with the drive sprocket 61 for rotation therewith, an internally splined clutch sleeve 72 axially slidably mounted on the hub member 71, an externally splined piece 74 fixedly mounted the right-hand hub portion of carrier 42 and a synchronizer assembly 73 coupled with the externally splined piece 74.
  • the clutch sleeve 72 is disengaged from the externally splined piece 74 to allow relative rotation between the drive sprocket 61 and the first output shaft 13.
  • the clutch sleeve 72 When shifted to and retained in a second position as shown by an imaginary line in Fig. 2, the clutch sleeve 72 is engaged with the externally splined piece 74 to rotate the drive sprocket 61 with the carrier 42 of center differential 40 thereby to extablish a four-wheel drive train.
  • the clutch sleeve 72 When the clutch sleeve 72 is shifted to the second position in a condition where the clutch sleeves 34, 55 are retained in their first positions, the drive torque from input shaft 12 is transmitted to the tubular output member 15 at a high speed, and in turn, the clutch sleeve 55 acts to directly transfer the drive torque from the output member 15 to the carrier 42 and the first output shaft 13 under the locked condition of the center differential 40 as described above.
  • the clutch sleeve 72 of third changeover mechanism 70 acts to transfer the drive torque from carrier 42 to the second output shaft 14 through the drive mechanism 60 to establish a high speed four-wheel drive train.
  • the clutch sleeve 72 of third changeover mechanism 70 acts to transfer the drive torque from carrier 42 to the second output shaft 14 through the drive mechanism 60 to establish a high speed four-wheel drive train, and the center differential 40 acts to effect differentiation between the first and second output shafts 13 and 14.
  • the clutch sleeves 34 and 72 of first and third changeover mechanisms 30 and 70 are shifted to and retained in their second positions as shown by the imaginary lines in Fig. 2 and that the clutch sleeve 55 of second changeover mechanism 50 is retained in its first position as shown by the solid line in Fig. 2, the drive torque from input shaft 12 is transmitted to the tubular output member 15 through the ancillary transmission 20 at a low speed, and in turn, the clutch sleeve 55 of second changeover mechanism 50 acts to directly transfer the drive torque from the output member 15 to the carrier 42 and the first output shaft 13 in a locked condition of the center differential 40.
  • the clutch sleeve 72 of third changeover mechanism 70 acts to transfer the drive torque from the carrier 42 to the second output shaft 14 through the drive mechanism 60 to establish a low speed four-wheel drive train.
  • the power transfer device is characterized in that the third change-over mechanism 70 is arranged between the planetary gear unit 40 and the drive sprocket 61 to selectively establish the two-wheel drive train or the four-wheel drive train.
  • the third changeover mechanism 70 With such an arrangement of the third changeover mechanism 70, the drive sprocket 61 can be mounted on the first output shaft 13 in a simple construction.
  • the second changeover mechanism 50 is characterized in that the clutch sleeve 55 is maintained in continual engagement with the internally splined portion 54 of side member 53 of ring gear 44 when shifted to and from the second position.
  • the translation length of the clutch sleeve 55 can be shortened, and the meshing engagement of the clutch sleeve with the externally splined portion 56 of first output shaft 13 and the internally splined portion 52 of carrier 42 can be smoothly conducted by only the right end chamfer of clutch sleeve 55.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Claims (3)

  1. Un dispositif de transfert de puissance agencé pour être utilisé en combinaison avec une transmission de puissance pour véhicule automobile, comprenant:
       un boîtier (11);
       un premier arbre de sortie (13) monté à rotation dans ledit boîtier, relié mécaniquement à un arbre de sortie de ladite transmission de puissance et comprenant une extrémité sortie reliée à un premier train de roues pour l'entraînement de ce dernier;
       un second arbre de sortie (14) monté à rotation dans ledit boîtier, en parallèle avec ledit premier arbre de sortie et comprenant une extrémité sortie reliée à un second train de roues pour l'entraînement de ce dernier;
       un élément menant (61) monté à rotation sur ledit premier arbre de sortie;
       un élément mené (62) monté sur ledit second arbre de sortie pour tourner avec celui-ci, et relié audit élément menant pour l'entraînement de ce dernier;
       un différentiel central (40) en forme de train épicycloïdal monté sur ledit premier arbre de sortie et comprenant un premier élément de sortie (41) monté sur ledit premier arbre de sortie pour tourner avec celui-ci et un second élément de sortie (42) monté à rotation sur ledit premier arbre de sortie pour être relié audit élément menant (61) pour l'entraînement de ce dernier; et
       un mécanisme de commutation (70) agencé entre ledit train épicycloïdal (40) et ledit élément menant (61) et monté sur ledit premier arbre de sortie (13) pour relier sélectivement le second élément de sortie du train épicycloïdal audit élément menant;
       caractérisé en ce que le premier élément de sortie dudit train planétaire est en forme de roue d'engrenage planétaire (41), que le second élément de sortie dudit train épicycloïdal est en forme d'arbre porte-satellites (42), et qu'un second mécanisme de commutation (50) est prévu pour transférer directement la puissance de la transmission de puissance, sélectivement, vers le premier arbre de sortie (13) ou une couronne dentée (44) dudit train épicycloïdal (40).
  2. Un dispositif de transfert de puissance selon la revendication 1, dans lequel ledit second mécanisme de commutation (50) est disposé adjacent audit train épicycloïdal (40) sur le côté opposé par rapport audit premier mécanisme de commutation (70) pour bloquer sélectivement ledit train épicycloïdal (40).
  3. Un dispositif de transfert de puissance selon la revendication 2, dans lequel ledit train épicycloïdal (40) comprend une pluralité de pignons satellites (43a, 43b) supportés par ledit arbre porte-satellites (42) et en prise avec ladite roue d'engrenage planétaire (41) et ladite couronne dentée (44) et en prise avec lesdits pignons satellites, ledit arbre porte-satellites (42) ayant une partie à cannelures intérieures (52) ménagée à l'une de ses extrémités et une partie formant moyeu tubulaire formée à son autre extrémité, entourant ledit premier arbre de sortie (13) pour le relier mécaniquement audit élément menant (61), et ladite couronne dentée (44) comprenant une partie à cannelures intérieures (54) formée à l'une de ses extrémités, et dans lequel ledit second mécanisme de commutation (50) comprend un manchon d'accouplement à cannelures extérieures (55) monté glissant axialement sur un élément tubulaire (15) en entourant ledit premier arbre de sortie, ledit manchon d'accouplement (55) étant maintenu constamment en prise avec la partie à cannelures intérieure (54) de ladite couronne dentée et pouvant être commuté entre une première position, dans laquelle il est engagé sur une partie à cannelures extérieures (56) dudit premier arbre de sortie et la partie à cannelures intérieures (52) dudit arbre porte-satellites (42) et une seconde position dans laquelle il est dégagé de la partie à cannelures extérieures (56) dudit premier arbre de sortie et de la partie à cannelures intérieures (52) dudit arbre porte-satellites.
EP92307919A 1991-09-02 1992-09-01 Dispositif de transmission de puissance pour entraînement à quatre roues motrices Expired - Lifetime EP0531088B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP221567/91 1991-09-02
JP22156791A JP2979762B2 (ja) 1991-09-02 1991-09-02 遊星歯車式差動装置
JP267222/91 1991-09-17
JP3267222A JP3003330B2 (ja) 1991-09-17 1991-09-17 四輪駆動車用動力伝達装置

Publications (2)

Publication Number Publication Date
EP0531088A1 EP0531088A1 (fr) 1993-03-10
EP0531088B1 true EP0531088B1 (fr) 1995-06-28

Family

ID=26524387

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92307919A Expired - Lifetime EP0531088B1 (fr) 1991-09-02 1992-09-01 Dispositif de transmission de puissance pour entraînement à quatre roues motrices

Country Status (4)

Country Link
US (1) US5286238A (fr)
EP (1) EP0531088B1 (fr)
AU (1) AU657069B2 (fr)
DE (1) DE69203183T2 (fr)

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US5380255A (en) * 1993-01-26 1995-01-10 New Venture Gear, Inc. Transfer case for part time front wheel drive in a four wheel drive motor vehicle
US5499951A (en) * 1993-08-02 1996-03-19 Borg-Warner Automotive, Inc. Dynamic range shift transfer case with electromagnetic clutch for coupling one output to the input for modulating torque split
US5718653A (en) * 1993-08-02 1998-02-17 Borg-Warner Automotive, Inc. Differential assembly for transfer cases and vehicle drivelines
US5584776A (en) * 1995-03-24 1996-12-17 Borg-Warner Automotive, Inc. Transfer case having parallel clutches and lockup feature
US5989146A (en) * 1997-03-21 1999-11-23 New Venture Gear, Inc. On-demand four-wheel drive transmission
DE69802598T2 (de) * 1997-03-21 2002-07-25 New Venture Gear Inc Vierradantrieb
US6142905A (en) 1997-03-21 2000-11-07 New Venture Gear, Inc. Full-time four-wheel drive transmission with limited slip clutch
AT405157B (de) * 1997-07-01 1999-06-25 Steyr Daimler Puch Ag Zweistufiges verteilergetriebe für ein kraftfahrzeug
US6579204B2 (en) 1999-03-09 2003-06-17 New Venture Gear, Inc. Synchronized two-speed transfer case with lockable limited slip differential
US6283887B1 (en) 1999-03-09 2001-09-04 New Venture Gear, Inc. Transfer case with synchronized range shift and adaptive clutch control
AT5016U1 (de) * 2000-12-20 2002-02-25 Steyr Powertrain Ag & Cokg Verteilergetriebe mit kupplungseinheit zum verbinden zweier abtriebswellen und kuppelverfahren
US6709357B2 (en) * 2001-03-23 2004-03-23 New Venture Gear, Inc. Transfer case with tubular output shaft
DE10333945B4 (de) * 2003-07-25 2006-06-29 Daimlerchrysler Ag Allrad-Antriebsstrang
DE102007006025B4 (de) * 2007-02-07 2011-07-07 Audi Ag, 85057 Verteilergetriebe für zumindest an zwei Achsen angetriebene Kraftfahrzeuge
CN104728347A (zh) * 2015-03-17 2015-06-24 陕西法士特齿轮有限责任公司 一种机械输力减速器
US10479659B2 (en) 2016-10-24 2019-11-19 Ingersoll-Rand Company Mechanism to selectively fix or free planetary carrier of epicyclic gearbox
US11401661B2 (en) 2017-11-14 2022-08-02 J & J Green Paper, Inc. Recyclable composition for waterproofing paper utilizing a plant derived wax, pellets of the composition, recyclable waterproof paper laminate including the composition, recyclable hot beverage cup including the laminate, pod for making hot beverages including the laminate, and drinking straw including the laminate

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JPS61207219A (ja) * 1985-03-12 1986-09-13 Toyota Motor Corp 車両用動力分配装置
DE3600872C1 (de) * 1986-01-15 1987-09-03 Daimler Benz Ag Planetenraeder-Verteilergetriebe fuer Kraftfahrzeuge
DE3600875C1 (de) * 1986-01-15 1987-04-02 Daimler Benz Ag Planetenraeder-Verteilergetriebe fuer den Antrieb von zwei Fahrzeugachsen eines Kraftfahrzeuges
JPH0650682Y2 (ja) * 1986-10-02 1994-12-21 マツダ株式会社 遊星歯車式副変速装置
JPH0626375B2 (ja) * 1986-11-26 1994-04-06 日本電気株式会社 フツク信号伝送装置
JP2596931B2 (ja) * 1987-04-27 1997-04-02 マツダ株式会社 ４輪駆動車の動力伝達装置
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JPH0643567Y2 (ja) * 1987-02-20 1994-11-14 トヨタ自動車株式会社 四輪駆動車用動力分配装置における潤滑機構
JP2572064B2 (ja) * 1987-04-27 1997-01-16 マツダ株式会社 ４輪駆動車の操作装置
JPH0820002B2 (ja) * 1987-04-27 1996-03-04 マツダ株式会社 ４輪駆動車の操作装置
US5078660A (en) * 1991-04-23 1992-01-07 New Venture Gear, Inc. Transfer case limited slip planetary differential

Also Published As

Publication number Publication date
AU2210892A (en) 1993-03-11
AU657069B2 (en) 1995-02-23
DE69203183T2 (de) 1995-10-26
DE69203183D1 (de) 1995-08-03
US5286238A (en) 1994-02-15
EP0531088A1 (fr) 1993-03-10

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